Machine for fabricating long stock at successive linear portions



J. H. ROBERTS July 9, 1935.

MACHINE FOR FABRICATING LONG STOCK AT SUCCESSIVE LINEAR PORTIONS FiledOct. 25, 1928 7 Sheets-Sheet 1 INVENTOR Jos gall/H: f0erfs MATTQRNEY.

7 Sheets-Sheet 2 Z :7 Y a m m MW? v w H e \w sw 6N a .mm

J. H. ROBERTS Fild Oct. 25. 1928 July 9, 1935.

MACHINE FOR FABRICATING LONG STOCK AT SUCCES'SIVE LINEAR PORTIONS J. H.ROBERTS July 9, 1935.

MACHINE FOR FABRIGATING LONG STOCK AT SUCCESSIVE LINEAR PORTIONS FiledOct. 23, 1928 7 Sheets-Sheet 5 MTTQRNEY J. H. ROBERTS July 9, 1935.2,007,345

MACHINE FOR FABRICATING LONG STOCK AT SUCCESSIVE LINEAR, PORTIONS FiledOct. 23, 1928 '7 Sheets-Sheet 4 iNV ENTOR Z V J65 lr'fi3%5erfs F anATTORNEY J. H. ROBERTS I ,007,345 I MACHINE FOR FABRICATING LONG STOCK AT SUCGESSIVE LINEAR PORTIONS Filed 00 0.. 23, 1928 (Sheets-Sheet 5INVENTOR v @x l- ATTORN EY.

July 9, 1935..

J. H. ROBERTS MACHINE FOR FABRICATING LONG STOCK AT SUCCESSIVE LINEARPORTIONS Filed Oct. '23, 1928 7 Sheets-Sheet 6 I [Illa Fm It i;ATTORNEY.

July 9, 1935- J. H. ROBERTS MACHINE FOR FABRICATING LONG STOCK ATSUCCESSIVE LINEAR PORTIONS Filed 001:. 23, 1928 Z Sheets-Sheet WW -lii--Patented July 9, 1935 OFFICE MACHINE FOR FABRICATING LQNG STOCK ATSUCCESSIVE LINEAR PORTIONS Joseph H. Roberts, Waterbury, Genre, assignorto The F. B. Shuster Company, New Haven, Conn, a corporation ofConnecticut Application October 23, 1928, Serial No. 314,388

62 Claims.

This invention relates to machines for fabricating long metal stock suchas rods, tubes or fairly thick Wires or flat long relatively narrowsheets wherein the stock, as it travels linearly thru the machine, issubjected to a fabricating operation or successively to a plurality offabricating operations such as punching, shearing, etc., particularlywhere any such kind of fabrication is effected on successive portions ofthe length of the stock which are uniformly separated from one another,as in the exemplary machine of the drawings where the stock wire, tubeor rod in this example is fed to shearing apparatus which operates sothat uniform lengths are cut successively from the successively forwardend portions of the stock, notwithstanding that the shearing apparatusis reciprocatory and moves rearward in a direction opposite to the feedof the stock as a preliminary to the shearing operation which isconducted while the stock is in its normal feeding motion without anystoppage or slowing up relative to the motion of the shearing mechanism;the shearing apparatus at the instant of shearing moving in the samedirection as the stock and at substantially the same rate.

More specifically the invention relates to such machines as the abovewherein the. metal stock is subjected to the action of straightening orleveling means as it is being fed to the shearing mechanism or to orfrom other fabricating devices.

The object of the invention is to improve the construction and operationof the above types of machines, i. e., machines for fabricating longstock at successive linear portions.

In accordance with the present invention and in the exemplary machine,the stock is fed continuously without stoppage to permit shearing whilethe stock is stationary as heretofore commonly practiced, the shearingbeing effected by a light-weight traveling, flying or aerial mechanismwhich intermittently is given an excursion which is short as to distanceand time, and involves both horizontal and vertical motions atsuccessive occasions after intervals of its rest while the continuousfeed of most of thelength of the stock oc curs, the stock continuing tobe fed also during such excursions of the shearing mechanism andcontinuously as long as the machine as a whole is in operation. Andduring each of such short excursions of the light aerial shear thelatter is operated to cut off a portion of the forward end of the stockwhile the entire length of the stock in the main portion of the machineis in feeding motion. Furthermore the successive cut short justments areprovided so that the operator at will can select any desired lineardimension within Wide limits for the uniform lengths of the cut stockfor a given job. This operation of the light aerial shear avoids theneed of interrupting the stock-feed and thereby permits an increase ofabout three inches of stock-feed for each shearcut as compared with theprior machines wherein the stock-feed was intermitted to permit shearingby mechanism which did not travel with the stock; so that, assumingabout twenty cuts per minute, from stock moving from about '75 feet andupwards per minute. there is an increased output from the new machine ascompared with such a machine having a stationary shear of about fivefeet of stock per minute, which amounts to an increase per day of two orthree thousand feet of stock per machine without any speeding up of themachine including the stock-feeding means to an undesirable degree.

The invention consists of the structural improvements and combinationspointed out in the claims and disclosed by way of example in thedrawings which comprise various views of one machine including Fig. lwhich is a front elevation of the main left-hand portion of the machine,in which the stock is fed from left to right;

Fig. 2 a front elevation of the right-hand continuation of the left-handor main portion shown in Fig. 1, Fig. 2 showing the means for receivingand the means for discharging the relatively short lengths of stockwhich have been sheared;

Fig. 3 an end View of Fig. 2 not showing the main or left-hand portionof the machine shown in Fig. 1;

Fig. l a detail of the assembly of the stock-receiving and dischargingapparatus of Figs. 2-3; Fig. 5 a plan of the main machine of Fig. 1;

Fig. 6 an elevation of the left end of the main machine of Fig. l, thefront with operators controls being shown at right;

Fig. 7 a vertical section of Fig. 1 at l'|, looking toward the left;

Fig. 8 a rear elevation of Fig. 1;

Fig. 9 a view of flyer D of Fig. 1, being a comparatively enlargedshowing of said flyer which is a rotary straightener;

Fig. 10 a section of flyer D partially in elevation;

Fig. 11 a perspective of one of the die-holders 22 for said flyer D;

Fig. 12 a perspective of the die or wearingpiece 2| for such holder 22;

Fig. 13 an end view of Fig. 12;

Figs. 14-16 detailed views showing assembly of die 2| in holder 22;

Fig. 17 a sectional detail assembly showing the relative positions ofthe parts of the fabricating or shearing apparatus in their normalpositions of rest just before commencement of their intermittent cycleof operations;

Fig. 18 a diagrammatic showing of the operations of the shearing-dies;

Fig. 19 a sectional detail assembly viewed facing Fig. 1 showing theslave apparatus L of Fig. 5 from the front including the roll-lockingclutch and associated apparatus controlling the timing of the repetitionof the fabricating operation as by the horizontal excursions of theshearing members shown in Figs. 17-48; and

Fig. 20 an elevation partly in section showing sufiicient of the lowerpart of die-carrier 34 of Fig. 17 to illustrate the operation of thelatter in re-latching or re-cocking the clutch or slave apparatus ofFig. 19 which performs the work of heavy duty.

In the exemplary machine disclosed, adapted for stock of variousdiameters, the general construction and operation are as follows. Ihemetal wire tube or rod of given diameter constituting the stock to befabricated or long metal sheets may be treated in a machine embodyingvarious of the principles of the exemplary machine usually comes incoils, the stock in each coil being several hundred feet long more orless and weighing several hundred pounds more or less. The operatorplaces one of these coils on the tilting reel A, Fig. 1 at left. Or thestock need not be coiled but may come directly from other manufacturingsteps to the operations of a machine embodying various features of thepresent invention. The operator then inserts the free or crop end of thereeled stock thru guide B and pushes it forward to a position enteringbetween horizontal rolls C, Figs. 1, 5-6 and 8, to be gripped therebyand thereby preliminarily straightened and fed rightward to and thrurotary flyer D where it is straightened finally whence the stock is fedbeyond D into position entering between a pair of auxiliary and largerdiameter horizontal feed-rolls C which feed the stock both by pulling itthru D and by pushing it to the fabricating, in this case shearing,mechanism at the right of C in Figs. 1, 5 and 8. After the machine hasbeen set in operation for a given job it is kept in operation while theoperator loads successive stock-rolls on reel A at left. Before startingoperation the rolls C and C are adjusted properly to grip the stock ofgiven dimensions by manipulating the wheels 20 so as to insure uniformcontinuous feeding from the stock-coil on reel A forward thru fiyer D tothe shearing mechanism at the right. The stock after being preliminarilystraightened by rolls C at left is pushed by them so that its forwardend, right, enters and passes thru the hollow rotating flyer D, Figs. 1,9-10, wherein by the contained offset dies E the stock is straightenedfurther and finally. In the beginning of operations on a fresh roll ofstock, as the forward end emerges from the right end of fiyer D, beingpushed by rolls C, it engages and is gripped by the auxiliary rolls Cwhich are pinch-rolls of large diameter, but rotated with the sameperiferal speed as rolls C, which thereafter insure that the rest of thelength of the long coiled stock is pulled thru flyer D and is fedcontinuously rightward to the fabricating mechanism, herein shown asshearing mechanism at the right, Figs. 1 and 5. During the feed of mostof the stock from a given stock-coil on reel A the rolls C cooperatewith the rolls C in the continuous uniform stock-feed. And the tail endof the stock-coil on reel A is pulled rightward by rolls C thru flyer Dafter the rear end of the stock has passed beyond rolls C; rolls C thenpushing such tail-end thru the fabricating mechanism adjacent (right of)rolls C As the successive linear portions of the long stock are pushedrightward by the tractive contact of their rear portions with rolls Cthey pass thru the orifice in shearing die G and underneath die I-I,Figs. 1, 5 and 17; or the stock passes thru the action of a sawing orcutting tool; or the stock first before reaching the shearing mechanismshown may be engaged by other fabricating mechanism such as a punch anddie, not shown but resembling the disclosed shearing mechanism in thegeneral principles of operation and control hereinafter described,followed by the above shearing, sawing or cutting operation as a finalfabrication prior to discharge from the machine; the stock movingcontinuously rightward thru die G and beneath die H, shearing members,to the stock-guides I, J, Figs. 2-4. At a certain point of the rightwardstock-feed the shearing members G, H commence the leftward movement of acomplete horizontal excursion from and back to their normal state ofrest shown in Fig. 1'7, and during such leftward movement the die H iselevated, higher than in Fig. 17, as in a pile driver in preparation forits subsequent downward shearing hammer blow here effected by a positiveforceful downward drive of the light-weight die H; the striking of thestock by die H in its said downward movement occurring at a certaininstant during the horizontal rightward return of G and H to theirnormal positions of rest; the downward movement of H occurring after adesired length of the stock has been fed by rolls C between guides I, J;and die H being forced downward positively by the comparatively heavyfly-wheel 5| Figs. 1 and '5, while the light-weight shearing mechanismis moving rightward with the stock, so that thereupon a short lengthfrom the forward portion of the stock is sheared off by dies G and H,such short length then dropping down into receiver M, Fig. 3, as acompleted product of the machine here shown. Thereupon dies G and Hcomplete the rest of their horizontal excursion by moving furtherrightward to their normal positions of rest in preparation for the nextshearing operation on a rear portion of the long unsheared stock whichmeanwhile and after the first shearing operation is fed from reel Atoward the point in its horizontal linear course where die H again isforced down for shearing during its rightward movement withvertically-stationary die G. Later descriptions will disclose the entireconstruction of the light aerial shearing mechanism.

The construction and operation of the apparatus on which are placed thecoils of stock to be fabricated are as follows, including particularlythe tilting reel or drum A which carries the stockcoil, Figs. 1, 5, 6and 8, reel A being shown in its normal position in which the plane ofthe reel and stock-coil are horizontal and the horizontal feed-rolls Care pulling the stock from the coil into the machine. When all the stockof a given coilhas been pulled by rolls C from off A the operatorwithout stopping the machine, which continues to operate onthe rearportions of such coil, removes pin I6 which normally holds reel-handle Hto machine-bed Q; and he then turns handle i i on its pivot P aquarter-revolution anti-clockwise from the twelve oclock position shown,Fig. l, to a nine oclock position where part HA of reel A rests on thefloor, the counter-weight i2 thus going to three oclock. The heavystock-co-ilnext to be fabricated then conveniently is moved from thefloor to a position encircling reel A in its lowered position.

Thereupon the operator by handle ll aided by counterweight i2 raises,via pivot P the stockcoil on drum A into the position shown wherein theplane of the drum is horizontal and its axis vertical, the part 52Aintegral with l2 abutting against frame Q. If desired the'axis of drum Ain its raised position may be horizontal or at any angle betweenvertical and horizontal to adapt it to other feeding arrangements. DrumA may be of any desired construction.- When the stockcoil is on reel Ain the position of the latter shown then the operator replaces pin illfor looking and inserts the free end of the rolled stock thru guide Band pushes it between the first pair of rolls C. I

' Feeding and straightening Rolls C are for initial stock-feeding andthe staggered ones intermediate the end-rolls for preliminarystock-straightening, the rolls C to the right, Figs. 1 and 5, being forfinal feeding after final straightening in flyer D. Initialfeeding,pinch, rolls C, first and last pairs, have vertical spindles and, Fig.5, are arranged, 'in the rod machine disclosed, all in the samehorizontal plane and in two rows on opposite sides of the path of thestock, being periferally grooved, Fig. 1, to receive the rod or wire.The same applies to the intermediate flattening rolls. The rolls intheba'clr row, Fig. 5, are mounted on spindles mounted. in fixed,roll-support 13. The spindles of the rolls in the front row are mountedin bearing-boxes or movable supports iii-45 which are adjustabletransversely of the machine to and from the rear rolls by operatorswheels Zil, at left, Fig. 5. All the spindles of rolls C in both rowsare rotated positively by a series of intermeshing gears Isa-15D, seepitch circles, Fig. 5, via ISD driven by worm-gear reduction unit W Fig.1, as will be described. The transversely adjustable'box-supports M, I5for the front row of rolls C are six in number, three pairsyand areadjusted 'by the siX threaded screws ll, Fig. 5, turned by,,wheels 29;screws 51 being journaled in side plate E8 of roll support l3. Spurgears 19 are mounted on screws H and mesh with spur gears ZQA, Fig. l,turnedby wheels 29 to adjust the front-row rolls toward the rear-rowrolls and the stock between front and rear straightening rolls.

After the stock leaves the last of rolls C at the right it is pushedandfpulled thru hollow rotary flyer D by rolls C and C respectively forfurther and final straightening in D by passing thru dies E, therein,Fig. 10, staggered or offset with respect to one another in decrescentdegree from left-to right in direction of stock-feed left to right.During the progress of the stock thru the staggered dies E the latterare rotated by belt R which rotates D thereby kneading the stock andexecuting the final straightening operation. Eachof dies E includes asteel holder 22, Fig. 11,

containing a removable, renewable wearing piece 2!, Figs. 12-14 and 16,preferably of non-ferrous metal, as brass, which is'grooved, as shownfor example, to conform with the diameter of the stock to be fabricated.Each Wearing member 2! is locked in its hardened steel holder 22 by thehinged part'of 22 shown. Clamping screws 23, Figs. 9-10, are adjustableto permit the adjustment of dies E to their staggered or offsetpositions shown, at the right, at the end of the final straighteningoperation, the last two dies being almost in alinement. The hexagonalcross-section of each wearing member 2| provides asubstantially solidseat for engaging the holder 22 diametrically opposite each of the threegrooves and provides an advantageous means of locking member 2! inholder 22. The drawings show clearly how '21 is locked in place upon theclosing of the hinged portion of 22. The construction of El permitscheap manufacture from long brass stock by sawing off short lengthstherefrom for each piece 2 i, such long stock before being sawed uphaving been fabricated as a whole in suitable mills to have the generalhexagonal cross-section shown. The sawed short lengths are ready for usein holders 22 without any further machining.

The three grooves in each piece 2! may be used successively by removing25 from the holder 22 and replacing it therein so that another groovecontacts into the passing stock (Fig. 10)

Horizontal feed-rolls or pinch-rolls C Figs. 1, 5 and 8, are two innumber gripping the stock between their grooved periferies; they aresubstantially larger in diameter than initial feedrolls C, and they arerotated in horizontal planes on their vertical spindles 3!, Fig. 5, byspur gears 21-33 from worm-gear reduction-unit Z, Fig. 1, as will be,explained. These rolls C are located in housing 2 1 having verticalcover-plate 33, Fig. 5. The rear roll is mounted vertically innon-adjustable position in housing 24. The front roll is adjustable withrespect to the rear roll being mounted in bearing boxes 25, 26 which areadjustable transversely of the machine by means of hand-wheel 2% whichoperates gearing which moves said boxes, as follows, Fig. 6. Wheel 20turns spur gear ZiiA between and meshing with spur gears 19 fixed onrotary adjusting screws 32, Fig. 1, the rear ends of which are threadedin the boxesf, 215 respectively so that the latter carrying the frontroll is moved to or from the rear roll as wheel 26 is turned. The frontends of adjusting screws 32 are journaled, Fig. 5, in vertical plate 33of housing 24.

From fiyer D the rolls C feed the straightened stock to the shearingmechanism at the right.

Shearing An important feature of the present invention is theconstruction and arrangement of the shearing mechanism and its controlsby which the portions of the stock which are cut successively from itssuccessive forward ends are caused to be of uniform lengthnotwithstanding that the shearing mechanism intermittently participatesin the continuous feeding motion of the stock imparted by rolls 0 and CThis uniformity-mechanism includes a master and slave, each illustratedas combinations of mechanical elements.

The slave includes, for example, a roll-locking one-revolution clutch L,Figs. 5, 7, 8 and 19, preferably of special design which together withasthe shearing members or dies G, H to move them into positions toshear, and to do the heavier work of moving H downwardly actually toshear, the more or less thick metal stock, as steel.

The master preferably is a variable adjustable speed transmission K,Figs. 1 and 5, which is adjustable by the operator by graduatedhandwheel 65 for a given job of desired length of cuts and which tripsslave clutch L and starts it working to operate the fabricating membersat the time proper to insure the cutting or other fabrication atportions of the stock uniformly distant from one another; theconstruction of slave L furthermore being such that it always actsuniformly, i. the same time always elapses at a given oporatorsadjustment of master K for a given job between the instant when slave Lis tripped by master K and the instant when L forces down die H by heavyfly-wheel action actually to shear the stock; and master K is soconstructed and adjusted and coordinated with the feed of the stock thatat a given adjustment it always trips slave L at the instant when thesame length of stock has passed rightward beyond H onto guides I, J inpreparation for shearing, and causes dies G and H to produce successivecut lengths of the stock which have the same linear dimension. Thusmaster K in effect is a stock length measuring apparatus which lays outand directs the work to be done by slave L. While the latter and thecooperating driving parts possess ample mass for heavy duty yet therotating and reciprocating shear parts are of very low mass makingpracticable their intermittent starting and stopping and reversals ofmotion and a speed of one foot and upwards per second.

Discharge As soon as a right end of the stock is sheared off by thedownward movement, Fig. 17, of die H alongside vertically-stationary dieG while both dies are moving horizontally rightward with the travelingstock and at substantially the same rate, then the guides I, J areseparated from one another, J going down, permitting the out lengths tobe discharged by gravity into the trough formed by the arms M of thereceiving rack N, 0, Fig. 3. Also following upon the completion ofshearing then slave L, including the disclosed novel design ofroll-locking one-revolution clutch of Figs. 5, 7, 8 and 19, causes theraising of die H back into its normal position relative to die G Fig. 17there to remain during continuation of feed of the stock thru G andunder H. There, Fig. 17, in the positions of rest of both said dies theyawait, while most of the next length of stock is being fed, the nexttripping of slave L by master K. Before the next horizontal excursion ofdies G and H, during which H is to make its vertical excursion, the rearstock, from which a forward end has been cut, is fed rightward until theinstant of the next tripping of slave L by master K to effect theactions of G and H at times proper to shear another portion of the stockof the same length as that previously sheared.

Main power connections All the power-driven parts of the machine aredriven by prime-mover P, Figs. 1, 5 and 8, mounted withinmachine-pedestal Q. P may be any desired form of prime mover, preferablyan electric motor, which may be but need not be one of constant speed.From P a flexible multi-strand belt R extends upwardly, Fig. 1, drivingthe main shaft T, idler pulley S and flyer D, Figs. 5, 6, 8.

Pulley S, Figs. 1, 5 and 6, permits maintenance of proper tension onbelt R by operators adjustment of wheel III4 at the front of themachine. Pulley S is pivotally mounted in cradle 95 on stud 96, Figs. 1,5 and 6. Cradle 95 is mounted pivotally on stud 91 of bearing bracket98, Figs. 1, 5 and 6. Wheel I04 operates adjusting screw 99 to movecradle 95 and pulley S toward belt R. Screw 99 engages in swivel nut Iwhich is suspended pivotally by the two studs IOI. Screw 99 is supportedpivotally by pivot I02 held in position by collars I03. Pivot I02 issupported by bracket I secured to roll support I3.

Main shaft T, Fig. 1, middle, extends longitudinally from left to rightof the machine; is journaled in pillow-block bearings 48, Figs. 5 and 8,and is rotated by sheave-pulley 49, Figs. 1, 5, 6 and 8, over whichmulti-strand belt R passes.

Power is distributed from main shaft T to feedrolls C and C master K,adjustable speed transmission, and slave L, the one-revolution clutch,as follows.

To rolls C, Figs. 1, 5, 6 and 8, power goes from T via spur gears U, V,left of belt R, Fig. 5, and standard worm-gear reduction unit W, Figs. 6and 1; and a spindle W Figs. 1 and 6, is coupled to W, extends upwardlytherefrom and carries one, IBD, Fig. 5, of the intermeshing gears I6,IGD which drive rolls C. The vertical arrangement of the roll-spindlespermits employment of the standard gear reduction-unit.

To rolls C the feed-rolls auxiliary to rolls C, power from main shaft Tgoes via spur gears X, Y, Figs. 1, 5, 6 and 8, and worm-gearreduction-unit Z, Fig. 1, from which upwardly extends a spindle of one,21, Fig. 5, of the four intermeshing spur gears 2'I30, Fig. 5, whichdrive the two rolls C the pitch diameter of the gears being shown inFig. 5. Here again the vertical spindles of rolls C permit employment ofthe standard gear reduction-unit.

The same spur gears X, Y also convey power from main shaft T to masterK, the disclosed adjustable-speed transmission, via constant-speed shaft35, Figs. 1, 5 and 7; so that master K is driven indirectly byprime-mover P which also drives the feed-rolls C and C The only functionof master K is to revolve master-cam 66A at the rate which will controlthe production of cut stock of the desired uniform length.

To slave L, Figs. 5, 7, 8 and 19, power from main shaft T is delivered,Figs. 5 and 8, via bevel-pinion gear 50 mounted on the right end ofshaft T. Gear 50 meshes with heavy fly-wheel bevel gear 5!, Figs. 1, 5,7 and 8, which is mounted on fixed to clutch-drum 52 on quill-hub 52Athereof. This continuously rotating fly-wheel and drum 52 provide themoment of inertia which conveys ample shearing power to the light-weightaerial shear of Fig. 17. Normally said drum 52, Fig. 19, and gear 5Irotate idly without turning their concentric one-revolution shaft 42,Figs. 17 and 19, directly on which the one revolution clutch L ismounted so that one cycle of operation of the shearing mechanism iseffected for each of the intermittent single revolutions of the clutch.This shaft 42 of the clutch, Fig. 19, is the main shearing-shaft, Fig.17. But when master K trips slave L then gear 5| and clutch-drum 52cause a single revolution of shaft 42 which effects the desiredhorizontal movements of shearing members G and H along the stock-pathand also elfects the down and up excursion of die H which takes placemidway of the rightward movement of G and H so as to effect the actualshearing of the stock while said die H is moving horizontally with thestock in the same direction and at the instant when all three of G, Hand the stock are moving at substantially the same rate; altho saiduniform movement of die H with the stock is only during the very brieftime of the actual shearing operation as will be described withreference to Fi 18.

i M aster connections to slave The mechanisms of master K and slave Lwhich are interconnected to cause K to trip L to start intermittentshear-movements are as follows, Fig. 5.- Cam or eccentric 66A, Figs. 5,8 and 19, on disk Biiis revolved by master K, shaft B6 carrying 66,thereby engaging sliding detent ill, Fig. 19, of slave apparatus Lcausing, Fig. a slight right-'- ward movement of 61 (leftward in Figs. 8and 19) toward and against spring 68, compressing the latteigby whichmovement 61 is withdrawn rightward, Fig. 5, (leftwardin Figs. 8 and 19),from its normal position in which it looks clutch stopplunger 69, sothat the latter is pulled down by its spring 19 thereby withdrawing theupper end of plunger 69 from its normal position wherein stop nose 56Blocks clutch L and its shaft .2 from rotation by drum 52 always inrotation by fly-wheel gear 5i mounted thereon and driven by pinions 50on main shaft T. This sliding action of detent 61 starts the clutch inoperation to drive the shaft 42 and initiate the excursion of thefabricating mechanism including shearing tools G and H. Shaft Hi6 is thevariable-speed shaft ofthe master-mechanism K, and is adjusted todifferent speeds by graduated hand-wheel 65, Figs. 1 and 5, so that therate of revolution of cam 56A is that which causes tripping of clutch Lat the proper time to produce the desired length of sheared stock. Thescale of 65 may be marked on a dial geared down to the shaft of 65.

Slave connections to fabricator The mechanism by which power is conveyedfrom fly-wheel 5i and drum 52 of slave-clutch L to dies Gand H is asfollows,--this mechanism beginning to operate said dies forthwith when Lis tripped by K to operate detent 6! as above to cause clutch shaft 42to be rotated by the continuously-rotating fly-wheel 5i and clutch drum52. On clutch shaft 42, Fig. 19, is fixed an eccentric or cam 39 Figs.1, 8 and 17, and on the latter ismounted the die-carrier 34, so thatwhen 42 being the one-revolution shaft of slave-clutch L is set inrotation, then said carrier 34 is given a corresponding eccentric ormutating motion with both vertical and horizontal componentssothat die Hfixed in 34 is given movements likewise partially horizontal andpartially vertical. Die-H-carrier '34 slides. up and down thru a secondcarrier F for die G which is slidable horizontally and guided by gibs 31on stationary support 35 for all this light-weight aerial shearapparatus of Fig. 17 in cooperation with eccentrics 38-39; so that thehorizontal component of the movement of die-H- carrier 34 is permittedby the horizontal movement of die-G-carrier F. Die G is fixed to itscarrier F which has only horizontal movement so that G does notparticipate in the vertical movements of die H; but both dies G and Hare given horizontal movements while die H is being moved up and downall these operations being caused by the single rotation of shaft 42,and 4!], and its eccentric 39 by the one-revolution clutch L; the twodies G and H alwaysremaining alongside one another.

As soon as cam 66A of master K, Figs. 5, 8 and 19, is revolved past theend of slide 61, Fig. 19, then the compression of spring 68 moves detent6! partially to the right in readiness to permit the downward movementof carrier 36 to act to disconnect shear-shaft 42 and the driven memberof clutch L from clutch-drum 52 continuously driven by main shaft T viafly-wheel gear 5i. A brake ii is provided at the end of theone-revolution shaft 42, Figs. 1, 5 and '7, to prevent continuationofrotation of said shaft by the moment of inertia of the driven member ofclutch L and of the fabricating mechanism operated by said drivenmember, after disconnection of drum 52 from the fabricating mechanism,so that neither shaft 42 nor dies G or Hwill be carried beyond thepositions of rest, Fig. 17, which they occupy normally during thegreater part of the time, i. e., while the clutch L is not operatingshaft 42 and while the greater part of the stock-feedis taking place.Said brake includes drum ti and a flexible band 62 encircling it andlined with frictional material, such as leather, the band 62 beinganchored by stud E3 to stationary machine-member 36 and being adjustablevia bolt 6 passing thru the band terminals; Figs. 1 and '7.

Coordinated operation of fabricatorand feeding motion of stock Below isdescribed the mechanism of the exemplary machine by which dies G and Hare operated in cooperation with the stock-feeding means, or otherwisecoordinated with the stockfeed, so that the continuously moving stock iscut into equal lengths by the light aerial shear traveling for a verybrief time uniformly with the stock; and this includes the details ofmaster K and slave L.

Of the master K the variable or adjustable speed transmission in generalis of any desired design of such well-known general type of apparatus.In the present combination of such transmission with the light aerialshear G, H, etc., such adjustable-speed transmission, Fig. 5, includesfirst the constant speed shaft 35 driven by motor P, second theadjustable-speed shaft Hi6 journaled in the stationary frame shown andcarrying the tripper or master-cam 66A for starting the rotation ofshear-shaft 42 by slave-clutch L, and third any suitable means such asthat indicated in the drawings, Fig. 5, including graduated wheel 65 andmechanism interconnecting with K for adjusting the speed of shaft I55 tothat rate which is necessary to coordinate the reciprocations of dies Gand H to the rate of stock-feed so asto shear the stock into uniformlengths of the linear dimension desired, such adjustment being operatedas by the graduated hand-wheel 65 and associated parts, Figs. 1 and 5.The scale on Wheel 55, Fig. 5, is marked in feet or the like by themanufacturer of the machine during the initial operation thereof so asto indicate to the user the length of the stock-cuts by dies G and H foreach given adjustment of wheel 55 by the operator for a given job; suchscale markings indicating the coordination of the shear controls withthe two sets of feed-rolls C and C both positively driven by the sameprime-mover P which operates master K and slave L, and, via L, the diesG, H. Thus the operator by wheel 65 can adjust the machine to producethe desired uniform lengths of cut stock without changing the normalfeed of the stock by rolls C and C driven like the shear-controls bymotor P. When,,as here, motor P operates not only the feeds for thestock but also the stock-shearing mechanism itself, the rate ofstock-feed by C and C is immaterial; because if it be varied byvariation of P' there will be corresponding variation of the times ofoperation of the shearing mechanism, owing to the fact that the feedingand shearing apparatus are coordinated as shown; so that always therewill be a uniform distance between the points along the length of thestock where fabrication is effected.

The bevel gear withhorizontalaxis operated by wheel 65 is journaled inthe frame shown and operates adjusting member I68 to the driving ratio"of the twocone-faced pulleys shown on shafts 35 and 105 connected bybelt as shown specially designed tocooperate with the conefaces of thepulleys, all as well known.

The trigger" or master-cam 66A which trips clutch L is formed, Fig. 5,as part of a circular cam-disk 66 mounted on the end of adjustablespeedshaft 106 of the adjustable speed transmission of master-control K. Eachrevolution of cam 66A occupies a time during which a length of stock isfed thru the machine, which length corresponds with the reading of thescale on hand-wheel 65 in the position to which the operator may haveset said wheel for a given job.

Cam 66A, during a small arc of its revolution moves sliding detent 61,Fig. 19, to its retracted position to left from clutch-plunger G9 toinitiate the action of clutch L on dies G, H. Thereupon the cam iscarried past 81 and spring 68 moves 51 back to right in position to lockplunger 69 when the latter shall be raised by the downward movement ofdie-carrier 34, Fig. 20. Meanwhile the single rotation of clutch Lproceeds for just the time necessary for the horizontal movements ofdies G and H. This time is a very small proportion of the total time offeed of even the comparatively short cut stock-lengths, which normallyare of the order of ten to twenty feet long more or less. Hence duringmost of the revolution of tripper-cam 65A it is out of engagement withsliding-detent or sear 51.

The construction of slave L including the onerevolution clutch, Fig. 19,is such that the excursion of dies G and H is commenced instant- 1y uponor always at the same time relative to stock-feed after the action ofcam 66A in starting clutch-shaft 42 in rotation by clutch-drum 52 andfly-wheel 5i; and brake 6| insures that the normal zero positions ofdies G and H, Fig. 17, always are the same so that the distance andtherefore the time of their horizontal excursion to left and back toright always will be the same; that is, the time always will be the samefor a given rate of stock-feed but will vary with the latter. Due to theabove and to the fact that master cam 66A always trips slave clutch Lwhen the same length of stock has been fed since the last previousstock-cutting, the result is that the downward shearing movement of dieH against the stock always will take place after the same length ofstock has been fed since the preceding shearing operation. That is,altho the continuously fed stock moves forward a slight distance afterdies G, H commence their horizontal movements by commencement ofrotation of shaft 42 and continue to move forward during the extremelyshort time of the downward shearing action of die H, and altho theactual shearing is not effected until after the dies commence the returnof their horizontal excursions, yet the time interval between thetripping of clutch L and the actual shearing always is the same for agiven rate of stockfeed and for a given setting of graduated handwheel65 coordinated with the stock-feed, or for a given setting of any otherscale which is an index of the automatic measurements by the master K ofthe length of parts of the stock to be out. It is the construction andarrangement of the slave-clutch L and its combination with theshear-parts as shown whichpermlt said time interval to be always thesame for all stocklengths which are cut thruou-t a given job, bypreventing. any variation of the time interval, relative to thestock-feed, between the retracition of deter-1t 6-1, to left, Fig. 19,by master 66A and the commencement of rotation of shear-shaft 42 byclutch drum 52 and fly-wheel 5i, i. e., between the retraction of detent51 and the commencement of the cycle of operations of the shearing orother fabricating apparatus; the actual cycle of operations of theshear-parts after commencement by shaft 42 always occupying the sametime relative to the stock-feed.

It is to be noted especially that in accordance with my inventions thedetent or sear 61 or its equivalent in causing initiation of the cycleof the shearing or other fabricating mechanism may be operated by theforward end or van of the stock, instead of cam 66A as a part of masterK, such generic master-control device, as detent 61, in such specificcase being struck as a target by the stock-van to initiate the operationof a shearoperating member as 42 by a power device such as slave L; suchstock-van operation of targetcontrol in general being disclosed in myco-pending application for patent Serial Number 291,651

led July 10, 1928.

The construction of slave-clutch apparatus L which causes commencementof the cycle of the shearing apparatus substantially instantly upon thetripping by the master cam 66A, or at least always at the same timeafter such tripping for a given rate of stock-feed, is as follows, seeFigs. 5, 7, 8 and 19. Primarily this clutch L preferably is of theroll-locking type shown, altho it may be of other types aselectromagnetic but in the present embodiment and combination there arevarious novel features which are included in the following descriptionand shown in the drawings. When master-detent 61 has been withdrawn fromstop-plunger 69, to left, Fig. 19, the latter is free to be and ispulled down by its spring 10 out of engagement with and in front ofstop-nose or lug 56B integral with basket 56 for locking-rolls 51, Figs.5, 7, 8 and 19. This causes normallyrotating clutch-drum 52 to beclutched to clutchbody 55 fixed to shear-shaft 42 for operation ofshearing-dies G, H. The detent slide 51, its spring 68, theclutch-plunger 69 and the contact disk 12 engaged by master-cam 66A arehoused in a casting 13, being retained in place therein by cover-plate14. Screw 1| is provided for regulating the tension of spring 68'. Rolls51 are moved radially outward to lock drum 52 to body 55 and shaft 42splined thereto at 34. Basket 56 for rolls 51 is mounted rotatively onextending hub 55A of clutch-body 55, being retained on said hub by plate58, Figs. 5, '1 and 8; and said plate being held in place by theadjustable nut 59 on the reduced end of clutch-shaft 42. When plunger 69has been pulled down from in front of nose 5613 the basket 56 is freefor rotation and is rotated, Fig. 19, clockwise by automatic means to bedescribed, and such rotation causes fingers 56A, one for each roll 51and engaging between ring 53 and the perifery of clutch-body 55. to moverolls 51 both circumferentially andradially outward along inclines 55Cin hardened steelclutchbody 55 into their cooperating recesses 553 insaid clutch-body to effect the positive locking of clutch-drum 52 tobody 55 and shaft 42, so that forthwith there is established a positivedriving linkage between fly-wheel 5| and drum 52 on the one hand andshaft 42 and shearing dies G, H on the other. Ring 53 is a hardenedsteel liner of overhanging cup 52B.

Thus the normally idle shear-shaft 42 intermittently is locked to thecontinuously rotating heavy fly-wheel driving-gear 5| for time intervalswhich are brief relative to the times of rest V, of 42; but each of suchbrief times is sufficient to allow a complete rotation of 42 and acomplete shearing excursion of dies G and H to act on the travelingstock.

The means for turning basket 56 when the latter is released by cam 66A,detent B1 and plunger 69, is the helical spring 6|), Figs. 5, 7 and 8,arranged around the outside of basket 56. One of its ends is anchored toplate 58, Fig. 8, and the other to basket-lug 5613. Spring 60 alwaystends to rotate basket 56 clockwise. Initially it is put under stress bythe constructor who turns plate 58, to which one end of spring 60 isanchored, until the desired stress is produced and then a pin, notshown, is passed thru plate 58 and into one of the holes |0'|A, Fig. 19,to hold plate 58 against being moved radially by spring 50. Then nut 59on the end. of shaft 42, Fig. 5, is tightened against plate 58. Thearrangement of spring 50 on the outside of basket 56 not only makes iteasy of installation, adjustment and inspection but permits it to have alarge diameterusefful in acting quickly to turn basket 56 and lock drum52 positively to clutch-body 55. I

All the above initiation of rotation of shaft 42 by massive driver 5|and drum 52 occurs in a very short time indeed, very much shorter thanthe brief moment of rotation of shaft 42, and always in the same lengthof time for a given rate of stock-feed, i. e., between the instant ofthe tripping action of cam 66A on sliding detent 61 and the immediatelysubsequent instant when clutch-body 55 begins to rotate shaft 42'anticlockwise to start the cycles of dies G, H from their normalpositions of rest, Fig. 17. During the single complete rotation of shaft42 which effects the complete horizontal excursion of G and H, theplunger 69, Fig. 19, has been moved upward in opposition to its spring10 to resume its normal relatched or re-lockecl position in the path ofthe clockwise revolution of stop-nose 5613. This normalposition of 69 isreached in advance of the complete revolution of said nose 55B and ofthe complete excursion of dies G and H; said relocking being effectedsubstantially while the stock is being sheared. As soon as said nose 56Babuts against stop 69 lying in its path, the rollbasket 56 disengageslocking-rolls 51 from their locking and driving positions betweenclutchdrum 52 and clutch-body 55 as above; and then clutch-body 55 andshaft 42, thereby disengaged from the positive drive via rolls 51,immediately come to rest under action of the braking means there toremain ready for the next single rotation of shaft 42 to effect the nextshearing excursion of dies G and If after the continuous feed hasadvanced sufiicient length of stock to require initiation of such nextexcursion of G and H, as de termined by the operators adjustment ofwheel 65. The heavy fly-wheel drive 5| for clutch-drum 5 2.providessufficient energy not merely to effect the horizontal excursions of diesG and H and the upward movement of H, but to insure the downwardmovement of H against the resistance of the more or less heavy stockundergoing shear mg.

Spring 60 isre-wound as the result of the above operations of stoppingthe intermittent movements of clutch-body 55, shaft 42 and the shearingapparatus; in fact, spring 80 cooperates with brake 6| in bringing saidparts to a quick stop. Just after plunger 69 is raised up in front. ofbasket-nose 55B, i. e. while rolls 57 are moving from their lockingpositions, and before said shearing parts come to rest, there is adefinite drift of said parts, i. e., about twenty degrees of rotation ofshaft 42. Spring 69 is wound up by that drift; and that action assistsin braking the parts.

Shearing mechanism The construction and operation of the mechanism bywhich dies G and H are operated by clutch-shaft 42 are as follows, thisinvolving what is termed herein the aerial shear. The main base 36 forthis light aerial shearing apparatus, Fig. 17 is fixed to heavy frame Qof the machine. The upper portion of base 36 is formed with ways or gibs31 on which slides die-G-carrier F which moves (reciprocates) only inparallelism with the feeding movement of the stock, first to left andthen back to rest at right. Carrier 34, shear-gate, for die H, mountedto slide vertically in the horizontally sliding die-G-carrier F is movedby clutch-shaft 42, which by means of the eccentric 39, Figs. 1, 8 and17, splined to shaft 42 by 43, imparts to said carrier 34 a movementwhich is partly vertical, to move die H successively up, down and up,and partly horizontal to move slide F and dies G and H horizontally,first to left opposite to movement of stock and then back to right withthe stock to normal positions of rest of the dies. The leftwardshear-movement gives time for H to be raised for its downward hammerblow to shear the. stock which occurs during the rightward movement of Gand H and at a midpoint thereof when the dies moving in the samedirection as the stock are moving also at substantially the same rate,i. e. during the instant after they have been accelerated to thestockrate and before they begin to be decelerated.

Thru the upper part of die-H-carrier 34 extends for symmetry with shaft42, an auxiliary shaft 40, Figs. 7 and 17, driven anti-clockwise bylower or clutch-shaft 42 via spur gears 44 fixed to 40, 45 fixed to 41,and 46 fixed to 42, Figs. 1, 5 and 7. These shafts 4|] and 42 arejournaled in bearings 36A of the main shear-carrier-support 36, Figs. 5and 7.

The intermediate gear 45 which drives upper auxiliary shaft 40 andeccentric 38, is mounted to rotate on stud 47, Figs. 1, 5 and 7, fixedrigidly'to stationary carrier-support 35. Upper or auxiliary shaft 40 iskeyed by key 4|, Fig. 17, to eccentric 38 which is a duplicate ofeccentric 39 fixed to shaft'42. Thus the two eccentrics 38, 39 extendingthru die-H-carrier 34 at top and bottom thereof respectively cooperatewith one another, intermittently rotating synchronously anti-clockwise,in imparting symmetrically the desired single cycle of eccentric motionto 34, partly vertical and partly horizontal. The rear end of up: pershaft 40 carries not only upper eccentric 38 but also a crank disk 90,Fig. 7, on which stud 9 i, Fig. 17, is mounted eccentrically to operatea pitman link 92 which operates the sheared sublengthdischarging-apparatus, especially movable guide, Fig. 4, in. a manner tobe described later. Thus such discharging. apparatus, in addition to theshearing apparatus, is operated thru slave L. and the eccentric-shafts42 and 40 all as timed by master K via cam 66A so that the cut stock isdischarged substantially as soon as it has. been sheared.

The operations of dies G and. H will be understood best. from thediagram of Fig. 18 in connection with Figs. 1'7. and 19-20. This diagrammakes clear the operation of the eccentrics 39, 38 and the dies orshearing members during the single rotation of shaft 42' and of theeccentrics -39 by slave L, and particularly the relative verticalpositions of G and H just before actual shearing (at A), at the time ofshearing at B, and after that at C and D until the parts come to rest atthree oclock of the dial which represents at its center the shaft 42 andat its perifery the eccentric 39-, the numerals of the dialcorresponding to the various positions of the eccentric 39, during therotation of shaft 42. The eccentrics, in the machine disclosed, have athrow of one and a quarter inches; that is, the distance ofhorizontaltravel of the dies in each direction of their excursion is twoand a half inches, i. e., between three and nine oclock of the diagramdial. The horizontal distances between the vertical lines pendant fromthe numerals represent the varying rates of the horizontal movement ofthe dies resulting from the eccentric action of die-H-carrler 34. Asabove, in the three oclock position of eccentrics 38, 39 relative toshafts 40, 42 respectively as centers, the dies are in their normalpositions of rest, as shown in Fig. 17, with die H at a level slightlyhigher than G. When shaft and eccentrics begin to turn anti-clockwisefrom three to nine oclock, Figs. 17-18, then both G and H are movedleftward, and during such leftward movement H begins at twelve oclock togo down on its shearing stroke while both G and H yet continue leftwardfrom twelve to nine oclock. By nine oclock H in its downward stroke hasreached a vertical position which is the same as that of its normalposition of rest, i. e.,. that shown in Fig. 1'7, three and nine oclock,Fig. 19', a level somewhat higher than vertically-stationary d'ie G, andhigher than at A, Fig. 18. Also at nine oclock both dies have reachedthe end of their leftward travel and commence the return trip of theirhorizontal excursion back to three oclock; the reversal of directiontaking place while H is going down and just prior to the vertical of Hat position A and prior to the actual shearing which occurs at aboutseven-thirty, at which shearing time the dies are moving rightward atsubstantially the same rate as the stock; the rate of return rightwardmovement between nine and eight oclock being less than the rate ofstock-travel as indicated by the horizontal distance between thevertical lines pendant from the dial numerals. As indicated by the firstpositions. of the dies, at A, in Fig. 18 the two dies are about inhorizontal alinement with one another as eccentrics 38-39 approach eightoclock, and rapidly are continuing to gain horizontal speed left toright, as shown by the spaces between the vertical lines from the dial,before shearing altho the dies yet are moving slightly more slowly thanthe stock; die H continuing to do down alongside and across die G. Asthe die-eccentrics or offsets 3839 have approached eight oclock, A, Fig.18, as above the die H has gone down to embrace the stock, its bottombeing open, and its effective lower edge is about to be jammed down uponthe stock to force (shear) off a sub-length along the vertical linebetween the adjacent dies. Between eight and seven oclock the horizontalspeed of the dies rightward is substantially the same as that of thestock rightward, and die H at about seventhirty, B, Fig. 18, has gonedown part-way across the stock and its effective lower edge has clovenor fractured and sheared the stock so that the sublength at right beingsheared already is being carried down by the movable stock-support Jbelow described more clearly. At the instant of shearing, the dies G andH are moving rightwardly at the same rate as the stock, at B, aboutseven-thirty. Between eight and seven oclock the vertical movement of His of about the same extent as its horizontal movement. After theshearing the die H continues downward until at six oclock, C, Fig. 18,it reaches its lowest position, both dies moving horizontally rightwardbetween seven and live oclock at a higher rate than the stock. At sixoclock while both dies are moving rightward at highest rate, die Hstarts moving upward and continues so to do, D, Fig. 18, until both diescease their horizontal excursion at three oclock at the end of theirrightward movement and there assume their normal positions of rest shownin Fig. 17 where die H is at a level slightly above die G. The two diesalways remain in relatively parallel vertical paths for shearingcooperation alongside one another.

Considering the above operations in terms of quadrants of the Fig. 18dial, and of the vertical component of the movements of die H, the firstquadrant of the revolution of eccentric 39 and resultant quadrant ofdie-excursion, three to twelve oclock, raises die H from its normal orintermediate level of Fig. 17 to its highest level; the second and thirdquadrants, twelve to six oclock, depress die H from its highest to itslowest level A, B, C, Fig. 18, including the shearing midway of thethird quadrant; and the fourth quadrant, six to three oclock, D, Fig.18, raises die H from its lowest level to its intermediate level ornormal position of rest of Fig. 17. As to the horizontal movements ofboth dies, the first two quadrants, three to nine oclock, move themleftward and the second two quadrants, nine to three oclock, move themrightward back to rest. During the leftward movements of the two diesthe die H is raised from normal or intermediate levelto highest leveland back down to normal level; and during rightward movement, with thestock, the die H is moved down the rest of the way and back up to normallevel for rest. The downward movement of die H occurs thruout the secondand third quadrants, twelve to six oclock, i. e., during the time whenthe two dies are executing the second half of their leftward movementand are reversing and moving thru the first half of their returnrightward movement; altho the stock actually is not engaged by die Hunder the impulse of the fly-wheel 5! until after the dies havecommenced their rightward return. Altho the parts of the shear includingdie H are of low mass yet ample shearing power is applied to the metalstock because behind H is the large moment of inertia of heavy fly-wheel5| and clutch-drum 52, Fig. 19, backed by their positive drive by mainshaft T rotated directly by belt R of maindriver P.

The actual stock-shearing takes place practically instantaneously i. e.,during only a portion of the very brief time while the lower edge of thesolid upper part of die H is passing, B, Fig. 18, downwardly across theright-hand end of the stock-opening thru hollow die G; said totaldownward movement of said lower edge of die H being while the eccentrics3%, 39 in their-anti-clockwise oclock positions.

Thus the practically instantaneous shearing action occurs whenstock-path-crossing tool H is about mid-way between 9 and 5 oclock, i.e., when it is within approximately one-quarterrevolution of its extremeposition of movement vertically,

revolution are passing from their eight to seven i. e. of movement,(when as usual the stock is moving horizontally), in the directionacross the stock-path. The tool-carriers are arranged relative to thestock-path, asshown', so that the above operation is insured, bylocating the center of revolution of the revolving tool so that theshearing action is effected as stated above.

After the shearing has been completed and die H has gone down further toits lowest position at C, Fig. 18, said lower edge of die Hinstant- 1yis raised, as the eccentrics turn further beyond their six o'clockpositions anti-clockwise toward their three oclock positions, so as toraise die H clear of the forward end of the stock next to be shearedwhich end lies in or near the right-hand end of the stock opening of G.This clearing of die H from the path of the continuously fed stockoccurs relatively long before the rightward movement of the dies isstopped by the engagement of clutch-nose 563, Fig. 19, againststop E59in the anti-clockwise revolution of said nose, and by the action ofbrake 6i-62; because said clearing occurs very shortly after die Hstarts to move up from its lowest position at C, Fig. 18, six oclock,owing to the fact that the eil'ective lower edge of H is only slightlybelow the die G opening even in said lowest position of H, so that theearlier part of the last quadrant, six to three oclock, raises saidlower edge of H above the die G opening, so that before H climbs to itsnormal or intermediate level, Fig. 17, its lower edge is far above thedie G opening as is shown at D, Fig. 18. Furthermore, from a point justto left of seven oclock, just after the'actual shearing, to a point justto right of five oclock, about when clearance of die H has occurred, thedies are moving rightward'at a faster rate than the uncut stock, seedistance between pedant lines from dial-numerals, so that the van of thestock to be cut does not catch up with the left of die I-I while it isbeing raised for clearance until at least after H has slowed down in itsfinal movement upward and rightward toward its position of restaftertheoccurrence of clearance.

Cut-stock receiving means This includes, right, Figs; 1 and 2, twouprights N positioned on longitudinal member Blhaving flange 32 securedto bed-casting Q of the machine. Additional stiifening means between thetwo uprights N, N consists of longitudinal dead shaft 83; and this is astrong support for the right-hand one of the two stock receivers O, 0,Figs. 2-3. Two stock-guides, via, I, stationary, and J, movable, aresupported by uprights N. I is secured, Fig. 4, to the overhanginggoose-neck tops N of uprights N. J is pivoted to front and rearlowering-arms '84, Figs. 1-4, 5, 8, 17, by means of upper pivot studs85. Front lowering arm .84 is mounted pivotally on stud 8?, Figs. 2-3.Rear lowering arm E54 and operating lever 89 are'mounted on stud shaft83, Fig. 1.

Movable guide J is formed with stock-groove 85, Fig. 4, on its sideadjacent stationary guide I, groove 86 extending from end'to end of J.As the stock is fed rightward from the shearing mechanism its forwardportion is received between guides I and J.

Stock-discharging mechanism' As soon as the shearing mechanism cuts offthe front end of the stock, but before drum 52 of slave L isdisconnected from shaft 32, guide J is moved on its pivots 85 in adownward sweeping are generally parallelling the downward movement ofdie H and its carrier 34, the sheared short length of stock'ingroove 86being moved by J until-they both pass below and beyond the lateralrestraining effect on the stock of stationary guide I; then the stockdrops down out of groove 86 and falls in the trough formed by arms M ofthe receiving racks N and 0. That downward move-' ment of guide J takesplace forthwith upon the stock-shearing, see B, Fig. 18. Spring 94-,Fig. 17, thereupon lifts J back to its normal position against the ledgeN of upright N and adjacen stationary guide I. Said downward movement ofguide J to discharge the sheared stock is effected by the followingmechanism, Fig. 1'7, starting from the above mentioned stud 9|eccentrically mounted on crank disk carried by shaft ii] in the top ofcarrier 34, Figs. 7 and 1'7. The revolution of eccentric stud 9i actsthru pitrnan link 92 to dischargethe out stock, from its confinement asabove betwen guides 1 and J in groove 86, as soon as the shearing isdone, i. e., when eccentrics 38, 39 are moving from eight to sevenoclock,

Fig. 18, during the rightward movement of the dies, carrier 34 and link92. Since disk as is fixed to shaft 40, the stud 9| revolves once foreach operation of slave clutch L, i. e., once for each excursion of theshearing dies, as in the case of the revolution of master-cam 66A, Fig.5, save that it is the initiation of the excursion of the shearing dieswhich is caused by said cam, whereas stud 9| acts later to discharge thecut stockat about the time of completion of the actual shearing. Themounting of guide J, which is moved by the above connections ii),'98-92, is by the two front and rear lowering .arms 84, Figs. 1, 3, 5,8, 1'7; the front arm being pivoted on stud 81, Figs. 2 and 3, .and therear arm being fixed to'stud-shaft 88 to which also is fixed anoperating lever 89 which connects link .92 to pivoted front lowering arm84. Thus guide J can be swungdownwardly on front pivot 81 and on rearstud-shaft 88 to free the cut length of stock for its discharge bygravity, such movement of J, Fig. 17, being caused by the clockwisemovement of 89 by link 92 at about the instant when H has completed itsdownward shearing stroke in the seven-thirty oclock position, Fig. 18,of eccentrics 38, 39 relative to their shafts 40, 42. The right end oflink 92 is slotted at 92A, Fig. 17, so that after clutch L first startsto turn anti-clockwise the shafts d0, 42, and the disk 90 and stud 9|,said link 92 reciprocates freely without operating the lever 89. Later,when eccentrics 38, 39 are at about seven-thirty o'clock, Fig. 18, theleft end-wall of the slot 92A engages stud 93 of operating lever 89 andpushes it rightward to swing 89 clockwise on pivot 88stretchingreturn-spring 94 and depresses guide J by'swinging 84 down;this action taking place when eccentric stud 9| is moving anti-clockwisefrom about four-thirty to three oclock relative to shaft 40 after itsanti-clockwise revolution from its, position of rest in Fig. 1'7;eccentrics '38, 39 during the depression of guide J moving from aboutseven-thirty, Fig. 18, to six o'clock, at which latter time, theoperating lever 88 is substantially vertical and guide J is depressedfully. Then as eccentrics 38, 39 move from six to three oclock, stud 9|is moved from three to twelve oclock, its position of rest in Fig. 17,and the left wall of the slot 92A in 92 is moved leftward leaving 89free to be swung to left by spring 94 into its position of rest in Fig.17, thereby raising guide J up alongside guide I in position to receivein groove 86 in J the stock continuously moving from the left. Thedepression of guide J is only for an instant and this guide is raisedfully by spring 94 by the time there is any projection of the van of thestock to be sheared beyond die H to the right.

Cooking mechanism The above assumes the return of stop-plunger 69 up toits normal position of Figs. 19-20 during, before the end of, the aboveexcursion of dies G, H. This assumed operation is effected as follows,by an action of automatic re-latching or re-cocking of slave clutch L inpreparation for the firing of die H down at the stock by means of saidclutch when the trigger, detent 61, is pulled by the operation of masterK and its cam 66A. This re-cocking is effected by the above downwardmovement of die-H-carrier 34, twelve to six oclock, Fig. 18, prior tofinal upward movement of 34 which raises die H into its normal positionof rest shown in Fig. 1'7. Such downward movement of carrier 34 effectsthe upward return movement of stop 69 by the following mechanism. On thelower end of carrier 34 is fixed a wearing-plate 15, Figs. 17, '7 and20, which engages with roll 16 journaled in the bifurcated upper end ofspring-cushioned plunger TI reciprocating thru bearing Q Fig. 17, instationary part Q of the machine frame or bedcasting. The lower end ofplunger 11 is slotted, Fig. 20, at "A and a cross-stud 19 engages insaid slot, being fixed in the left end of lever 18; lever '18 beingintermediately mounted pivotally on short shaft turning, Fig. 20, in abearing member Q secured to machine-bed Q; and the right end of lever 18engages the lower end of clutch-stop 65. By this time master-cam 66A haslet go of detent 61, Fig. 19, and spring 68 has forced 61 rightwardagainst plunger 69; spring 68 standing by to push 61 further rightwardinto the locking recess in 59 as soon as upward movement of 69 carriessaid recess up into the horizontal path of 61. So, when die-H- carrier34 goes down, from twelve to six oclock, Fig. 18, the upper wall of slot11A in plunger 11 engages stud 19 to swing the left end of 18 down onits pivot 80 to lift clutch-stop 69, stretching spring 10, in positionin front of nose 56B and allow spring 68 to push detent 61 into thelocking recess in 69; and later, when nose 56B abuts stop 69 at the endof the effective rotation of L and of the excursion of dies G and H,then the locking-rolls 51 of the clutch are moved from their drivingpositions, and drum 52 of clutch L thereby is disconnected fromclutch-shaft 42 which constitutes the drive for G and H. Detent 61 insaid position locking stop-plunger 69 is ready to be retracted later bymaster cam 66A at the proper time to cause clutch L again to operatedies G and H via shaft 42. Slot HA in 1'! permits the final raising of34 and H, six to three oclock, Fig. 18, without disturbance of thepreviously effected re-cocking. Clutch L may be tripped manually by theoperator to cause shear-operation on the crop end of each long piece ofstock entering the machine; and any desired mechanism can be employedfor this purpose in addition to the automatic tripping mechanism shown.

Summing up the above shearing operations at the right of the machine inchronological order. starting from the state of rest in Figs. 17, 19-20at the three oclock positions of cams or eccentrics 38, 39 in Fig. 18,master cam 08A has a rate of revolution which is predetermined by thesetting of graduated wheel 65 to have a definite desired relation to therate of stock-feed; and said cam first trips slave-clutch L to initiatethe operation of the aerial shear including dies G, H. Then, just beforedie H reaches its lowest posi tion, six oclock, Fig. 18, and during theshearing the stock-guide J containing the sheared-off stock-length ismoved down by Sit-93 to discharge said length whereupon J immediately israised to normal by spring 94. And after said master-earn EtA has beenrevolved beyond detent 61, and while die H yet is moving down in itsshearing stroke, twelve to six oclock, Fig. 18, the

die-H-carrier 34 by its downward movement causes re-cocking of clutch Lnot only to prepare thereby to stop the shear operation but also to putthe parts in condition for the next tripping of the clutch by master cam56A after the feed of uncut stock has continued to the desired extent asdetermined by the adjustment of adjustable speed mechanism K by wheel65. And finally, with stop 69 in the path of the moving stop-nose 563,Fig. 19, the clutch L and its shaft 42 operate thru their last quadrant,six to three oclock,

Fig. 18, to move dies G and H thru the latter half of their rightwardstroke whereupon nose 56B abuts stop 69 to disconnect clutch-drum 52 andfiy-wheel 5| from shaft 42; and thereupon brake 6l62 with the re-windingof spring 60 stops the motion of the shear-parts driven by L at theirnormal positions of rest of Figs. 1'7, 19-20, 1. e., at three oclock,Fig. 18.

The relative rates of travel of the continuously fed stock and theintermittently moving shear are coordinated ultimately by the amount ofeccentricity of cams 38, 39; after general determination of such ratesby the power-connections from motor P and shaft T to feed-rolls C and Cvia standard gear-reduction units W and Z respectively and toclutch-shaft 42 via pinion 5D and flywheel gear 5l. With theabove-described eccentric-throw of one and one-quarter inches for cams38, 39, a desirable rate for clutch-shaft 42 and said cams is R. P. M.with a stock-feed by rolls C, C of about seventy-five feet per minute;this for the rod, tube, or wire machine disclosed; the rate ofhorizontal movement of die-G-carrier F at the instant of shearing, B,Fig. 18, being substantially the same as the horizontal movement of thestock. Thus, in any case, intermittent action of the shear involves itspractically instantaneous conversion from a state of absolute rest to arate of movement of from at least about a foot per sec0nd,an operationentirely practical with the arrangements including the lightaerial'shear-parts and the relatively heavy continuously operated clutchparts above discussed and specified in the following claims.

I claim:

1. In a long stock fabricating machine, the combination withstock-feeding mechanism; of a fabricating tool reciprocable both in linewith the direction of stock-feed and simultaneously to and from themoving stock; a member reciprocable in If intermittently tripping theclutch and fiy-wheel to cause revolution of said eccentric mechanism atdesired times. a

2. In a long stock fabricating machine, the combination withcontinuously operating stock feeding mechanism, of an intermittentlyoperating fabricating tool reciprocable both in line with the directionof stock-feed and simultaneously to and from the moving stock; a memberreciprocable in line with the direction of long-stock feed; a secondreciprocable member movable with the first and also simultaneouslyreciprocable toand from the moving stock; said fabricating tool beingmounted to participate in the movements of said second reciprocablemember; the reciprocating members beingcooperatively arranged rel ativeto one another to cause the reciprocation of the second member to effectreciprocation of the first thereby keeping the second and said tool freefor their said double reciprocation; revolvable eccentric mechanism onwhich said second reciprocable member is mounted whereby the said doublereciprocation is imparted to said fabricat ng tool; continuously drivenmeans for revolving said eccentric mechanism at a rate coordinated withthe rate of said stock-feeding mechanism but normally disconnected fromsaid eccentric mechanism; tripping mechanism intermittently causingconnection of the eccentric mechanism to its said revolving means; and amaster effecting intermittent operation of said tripping mechanism attimes coordinated with the feed of the long stock by said feedingmechanism. I 3. In a long stock fabricating machine, th combination withcontinuously operating stockfeeding mechanism, of an intermittentlyoperating fabricating tool reciprocable both in line with the directionof stock-feed and simultaneously to and from the moving stock;tool-carrying mechanism including two. reciprocable members of which oneis movable in line with the direction of long-stock feed and the otherof which ismovable to and from the movingstoclaone of said members beingreciprocable with the other but free for its own reciprocation, andconnected with the fabricating tool to cause saidreciprocations thereof;normally stationary mechanism intermittently effecting reciprocation ofsaid doublyreciprocable tool-carrying member causing said combination ofthe latter with the other reciprocable member to effect thereciprocation of said other reciprocable member, said mechanismeffecting such reciprocation being'normally at rest, and during most ofthe time of stock-feed said reciprocable members andfabricating toolalso being then at rest; and mechanismintermittently causing saidreciprocating mechanism tobecome operative at desired times;

4. In a long stock fabricating machine; the combination withcontinuously operating mechanism feeding theilong stock horizontally,of. an

intermittently operating fabricating tool reciprocable both horizontallyand simultaneously vertically; tool-carrying mechanism including twomembers of which the first is reciprocable horizontally and the secondof which is reciprocable horizontally together with the first and alsosimultaneously but independently reciprocable vertically and connectedwith the fabricating tool to cause said horizontal and verticalreciprocations thereof; normally stationary mechanism intermittentlyreciprocating said second or doubly-reciprocable member causing its saidcombination with the first reciprocable member to effect thereciprocation of the latter and the tool at a rate coordinated with therate of said stockfeeding mechanism; said reciprocation-producing Imechanism normally during the operation of the machine beinginoperative, said reciprocable members and fabricating tool also beingthen at rest; and mechanism automatically and intermittently-causingoperation of both said reciprocable members at desired times by means ofsaid reciprocation-producing mechanism. l

5. In a long stock shearing machine, the combination with stock-feedingmechanism, of two cooperating shear ng tools, the first of which is'nated with the rate of said stock-feeding mechanism; and trippingmechanism automatically and intermittently causing operation of saidrevolving means at desired times.

6. In a long stock shearing machine, the combination with continuouslyoperating stock-feeding mechanism, of two intermittently operating cooperating shearing tools; tWo tool-carriers for said tools respectivelythe first carrier-being reciprocable in the machine in line with thedirection of long-stock feed and the second carrier being movable withand reciprocable thru said first carrier in a direction to and from themoving stock; eccentric mechanism intermittently moving said carrier andthereby the first carrier thru which it moves, but idle during most ofthe z time of stock-feed; driving mechanism normally disconnected fromsaid eccentric mechanism but in continuous operation at a ratecoordinated with the rate of the continuously operating. stock feedingmechanism; and tripping mechanism intermittently automatically causingoperation of said eccentric mechanism at desired times by said drivingmechanism.

'7. In a long stock shearing machine, the combination with continuouslyoperating stock-feeding mechanism, of two intermittently operating andcooperating shearing tools; a member reciprocable in line with thedirection of long-stock feed and carrying one of said shearing tools; asecond similarly reciprocable memberlalso movable across the path of themoving stock; two

' synchronously revolvable but normally stationary eccentrics on whichsaid second reciprocable member is mounted; said two reciprocablemembers being arranged relative to one another to cause thereciprocation of the second member by the eccentrics to effect thereciprocation of the first member; the second shearing tool beingmounted to participate in the reciprocations of both said members;intermittently operating mechanism revolving said two eccentrics at arate coordinated with the rate of said continuously operatingstock-feeding mechanism; and a master causing occurence of saidintermittent operation of said revolving means at times coordinated withthe feed of the long stock by the feeding mechanism.

8. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism, of intermittentlyoperating fabricating mechanism reciprocable in line with the directionof long-stock feed and including a fabricating tool movable also acrossthe path of the moving stock; two parallel rotatable shafts; twoeccentrics arranged to be revolved by said shafts respectively;mechanism operated by said eccentrics and effecting single excursions ofsaid fabricating mechanism and said tool for each rotation of saidshafts; mechanism initiating synchronous rotation of both said shafts attimes coordinated with the feed of the stock by said feeding mechanismand at rates coordinated with the rate of said feeding mechanism; andmechanism stopping said shafts at the end of single rotations thereof.

9. In a shearing machine for long rods and wires, the combination withcontinuously op erating stock-feeding mechanism, of two intermittentlyoperating and cooperating shearing dies; two die-carriers for said diesrespectively, the first carrier being reciprocable in the machine inline with the long-stock feed and the second carrier being movable withthe first carrier and movable therethru in a direction across the pathof moving stock; eccentric mechanism on which said second carrier ismounted; driving mechanism intermittently effecting a single revolutionof said eccentric mechanism at a rate coordinated with the rate of saidcontinuously operating stock feeding mechanism; and mechanismcontrolling the times of operation of said driving mechanism incoordination with the stock-feed.

10. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism, of fabricating meansintermittently reciprocable in line with the direction of stock-feed andsimultaneously movable across the path of the moving stock; aroll-locking clutch causing said intermittent operation of saidfabricating means; said clutch having a member continuously rotating ata rate coordinated with the rate of said stock-feeding mechanism; acommon power source operating both said clutchmember and said feedingmechanism; and a master controlling the roll-lock of the clutch incoordination with the feed of the stock.

11. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism, of intermittently-actingfabricating mechanism reciprocable in line with the direction ofstock-feed and simultaneously movable across the path of the movingstock at rates coordinated with the rate of said stock-feedingmechanism; a roll-locking clutch arranged to effect such intermittentoperation of the fabricating mechanism; and a master controlling therolllock of said clutch in coordination with the feed of the stock. 7

12. In a long stock fabricating machine, the

combination with continuously operating stockfeeding mechanism, ofintermittently-acting fabricating mechanism including a fabricatingtool; a continuously-driven uniformly-acting and positive-locking clutcharranged to drive the fabricating mechanism and tool intermittently atrates coordinated with rate of the stock-feeding mechanism said clutchincluding a member rotatable to effect driving connection of the clutchwith the fabricating mechanism; a helical spring mounted exteriorly onand concentric with said rotatable clutch-member in condition normallytending to rotate the same; stop-mechanism normally preventing rotationof said clutch-member; a master intermittently causing operation of thestop-mechanism freeing said clutch-member for rotation by said spring attimes coordinated with the feed of the stock; and mechanism restoringthe normal position of the stop-mechanism and causing rewinding of saidspring for succeeding actions, such rewinding acting as a brake on thefabricating means during the operation of disconnection of the clutch.

13. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism, of intermittently-actingfabricating means including a fabricating tool; mechanism intermittentlyoperating said fabricating means and tool at rates coordinated with therate of said stock-feeding mechanism; a rotatable driver of saidreciprocating operating mechanism normally disconnected therefrom duringthe stock-feed; a spring tending to effect comiection of said rotatabledriver with said operating mechanism; means normally opposing saidtendency of said spring; a master intermittently freeing said spring forconnection of said driver to said operating mechanism for at timescoordinated with the feed of the stock by said feeding mechanism;mechanism causing disconnection of the driver from said operatingmechanism; and a brake stopping the operating mechanism and thefabricating means upon such disconnection.

14. In a long stock shearing machine, the combination with continuouslyoperating stool:- feeding mechanism, of gearing driving it and alongitudinal shaft driving saidgearing; a main driver; a belt from saidmain driver and driving said shaft; a bevel gear on said shaft; atransverse shaft; a bevel gear and a connected uniformly-acting,positive-locking clutch both on said shaft but normally idling thereon,said bevel gears intermeshing; fabricating mechanism driv-' en from saidtransverse shaft and including two shearing members both reciprocable inline with the direction of stock feed and one simultaneously movableacross the path of the continuously fed stock, and both operated by saidshaft at rates coordinated with the rate of said stockfeeding mechanism;tripping mechanism intermittently effecting operative connection of theclutch with its said transverse shear-operating shaft; a master causingsaid intermittent operation of the tripping mechanism at timescoordinated with the feed of the long stock by said feeding mechanism;and mechanism operated by said main driver and causing operativedisconnection of the clutch from its said transverse shear-operatingshaft.

15. In a long stock shearing machine, the combination with continuouslyoperating initial stock-feeding mechanism, gearing driving it and a.longitudinal shaft driving said gearing; a main drive; a belt from themain driver driving said longitudinal shaft; a bevel gear on said shaft;a transverse shaft; a bevel gear and a connected uniformly-acting,positive-locking clutch both on said shaft but normally idling, thereon,said bevel gears intermeshing; intermittently operating fabricatingmechanism driven from said transverse shaft and including two shearingmembers both reciprocable in line with the direction of stock feed andone also simultaneously movable across the path of the continuously fedstock; auxiliary stock-feeding mechanism continuously operating andlocated between the initial feeding mechanism and the fabricatingmechanism; both said stock-feeding mechanisms and said shearing membershaving rates of movement coordinated with one another; operativeconnection of the clutch with its said transverse shear-operating shaft;a master causing said intermittent operationsof the tripping mechanismat times coordinated with the feed of the long stock by said feedingmechanisms; and mechanism operated by said main driver and causingoperative disconnection of the clutch from said transverseshear-operating shaft.

16. In a long stock shearing machine, the combination with continuouslyoperating stockfeeding mechanism, of gearing driving it and alongitudinal shaft driving said gearing; a main driver; a belt from thelatter and driving said longitudinal shaft; a 'bevel gear on said shaft;a transverse shaft; a bevel gear anda connected uniformly-actingpositive-locking clutch both on said shaft but normally idling'thereon,said bevel gears intermeshing; fabricating mechanism intermittentlydriven by said-shaft at rates coordinated with the rates of saidstock-feeding mechanism and including two inter-related shear-carriershaving the shearingfmembers respectively mounted thereon, both saidshear-carriers being reciprocable in line with the direction ofstock-feed and one of them being also simultaneously movable across thepath of the continuously fed stock; eccentric mechanism revolved by saidtransverse shaft, one of said shear carriers being mounted on saideccentric mechanism; tripping mechanism intermittently effectingoperative connection of said clutch with its said transverseshear-operating shaft; a master causing said intermittent operation ofthe trip:- ping mechanism at times coordinated with the feed of the longstock by the feeding mechanism; and mechanism operated by said maindriver and causing operative disconnection of the clutch from its saidtransverse shaft.

17. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism feeding the long stocklengthwise in a straight line, of intermittently operating fabricatingmechanism including a fabricating tool reciprocable in line with thedirection of long-stock feed, said fabricating tool'being also movablesimultaneously across the path of the continuously moving stock;mechanism intermittently effecting such movements of said fabricatingmechanism and said tool at rates coordinate-d with those of saidstock-feeding mech-' anism, said mechanism including eccentric mechanismconnected to said tool and normally stationary in substantially threeoclock position relative to its center of revolution on the assumptionthat said straight line feed of the stock is from nine to three oclock;and driving mechanism intermittently effecting a single completeanti-clockwise revolution of said eccentric mechanism from its saidthreeoclock position whereby the fabricating toolfirst is moved opposite tothe direction of stock-feed while being first moved away from the stockand its normal position and then moved back to normal and toward thestock, and then its movement opposite to the stock-feed is reversed andit is moved in the same direction as the stock feed while being firstmoved from normal toward and acrossthe moving stock and then moved backto normal and out of the path of the moving stock beforethe rate of thetool in the direction of stock-feed becomes less than that of the stock.

18. In a long stock shearing machine, the combination with continuouslyoperating stock-feeding mechanism, of intermittently operating shearingtools both of which are reciprocable in line with the direction oflong-stock feed, one of them being also movable simultaneously acrossthe path ofthe moving stock; revolving eccentricmechanism intermittentlyeffecting such movements of both tools, said eccentric mechanismnormally being stationary in substantially three oclock positionrelative to the center of revolution on the premise of the stock beingfed along a straight line from nine to three oclock; and driving mecha--nism intermittently eifecting a single complete anticlockwise revolutionof said eccentric mechanism from its'said three 'oclock position wherebythe two shearing tools first are moved opposite to the, direction ofstock-feed while one of them is firstmoved away from the stock and itsnormal position and then moved back to normal and toward the stock, themovement of the two tools opposite to the stock-feed then being reversedto the same direction with the stock-feed while one of them first ismoved from normal toward and across the stock and then moved back tonormal and out of the path of the moving stock before the rate of thetool in the direction of stock-feed becomes less than that of the stock.

, 19. In a long stock shearing machine, the combination withstock-feeding mechanism, of intermittently-acting shearing mechanismincluding two shearing tools reciprocable in line with the direction oflong-stock feed, one of said tools being simultaneously reciprocablealso to and from the moving stock; mechanism effecting suchreciprocations of said tools; mechanism receiving the advanced portionof the stock fed beyond saidshearing mechanism; and dischargingmechanism connected between the shearing mechanism and receivingmechanism and moving the latter to discharge the sheared advance end ofthe stock.

20. In a long stock fabricating machine, the combination withcontinuously operating stockfeeding mechanism, of intermittentlyoperating fabricating mechanism reciprocable in line with the directionof long-stock feed and including a fabricating tool simultaneouslymovable also across the path of the moving stock; mechanismintermittently effecting such tool-movements; a drive-shaft mountedtransversely of the machine and operating said tool-moving mechanism; amain driver; connections with the feeding mechanism continuouslyoperated by the main driver; a roll-locking clutch between themain-driver and said transverse drive-shaft; and means intermittentlycausing operative connection of the main driver with the drive-shaft byway of said clutch and therefore operating the fabricating mechanism attimes coordinated with the movement of the stock by said feedingmechanism; the rates of said intermittently operating transverse shaft,tool-moving mechanism, fabricating mechanism and tool being coordinatedwiththose of said

